Turbine blade geometry

Abstract: A steam turbine blade is provided in which the geometry of the blade airfoil is configured to reduce the weight of the blade while maintaining adequate thermodynamic performance. The blade has a high camber angle to increase its stiffness and an airfoil portion having pressure and suction surfaces. The curvature of the portion of the pressure surface between 25% and 75% blade height has a point of inflection in an area adjacent the leading edge so that the curvature switches sign. The curvature upstream of the point of inflection is concave, while the curvature downstream of the point of inflection is convex.

Description: The present invention relates to blades for a steam turbine rotor. More specifically, the present invention relates to a light weight blade for use in the transition zone of a low pressure steam turbine that substantially reduces the centrifugal stress on the blade root and the rotor groove in which it is disposed. The steam flow path of a steam turbine is formed by a stationary cylinder and a rotor. A large number of stationary vanes are attached to the cylinder in a circumferential array and extend inward into the steam flow path. Similarly, a large number of rotating blades are attached to the rotor in a circumferential array and extend outward into the steam flow path. The stationary vanes and rotating blades are arranged in alternating rows so that a row of vanes and the immediately downstream row of blades forms a stage. The vanes serve to direct the flow of steam so that it enters the downstream row of blades at the correct angle. The blade airfoils extract energy from the steam, thereby developing the power necessary to drive the rotor and the load attached to it. Such a type of steam turbine is disclosed for example in the document US-A-5 203 676. The amount of energy extracted by each row of rotating blades depends on the size and shape of the blade airfoils, as well as the quantity of blades in the row. Thus, the shapes of the blade airfoils are an extremely important factor in the thermodynamic performance of the turbine and determining the geometry of the blade airfoils is a vital portion of the turbine design. As the steam flows through the turbine its pressure drops through each succeeding stage until the desired discharge pressure is achieved. Thus, the steam properties -- that is, temperature, pressure, velocity and moisture content -- vary from row to row as the steam expands through the flow path. Consequently, each blade row employs blades having an airfoil shape that is optimized for the steam conditions associated with that row. However, within a given row the blade airfoil shapes are identical, except in certain turbines in which the airfoil shapes are varied among the blades within the row in order to vary the resonant frequencies. Designing a steam turbine blade is made difficult by the fact that the airfoil shape determines, in large part, the mechanical strength of the blade and its resonant frequencies, as well as the thermodynamic performance of the blade. These considerations impose constraints on the choice of blade airfoil shape so that, of necessity, the optimum blade airfoil shape for a given row is a matter of compromise between its mechanical and aerodynamic properties. This situation is exacerbated in the transition zone of a low pressure steam turbine, such as that used in a boiling water reactor nuclear power plant, due to the high moisture content of the steam flow in that zone. Such high moisture content results in erosion and corrosion of the components exposed to the steam flow. Most importantly, for present purposes, this erosion and corrosion can weaken the blade, especially in the root area, as well as the rotor groove to which the blade is secured. Since the blade root and rotor groove are subjected to high stresses due to centrifugal force, the erosion and corrosion can result in cracking. Consequently, it is important that the weight of the blade be minimized, thereby minimizing the centrifugal force to which the blade root and rotor groove are subjected during operation. Reference is made to prior art document DE-A-3201436 which discloses a turbo-machine blade including a continuously curved profile contour having convex curved leading edge, suction side and trailing edge regions, and a concave curved pressure side region, the leading edge section being formed of a first ellipse section and a second ellipse section adjacent the first ellipse section; the suction side region being formed of a first circle section adjacent the second ellipse section and a first parabola section of a first second-order parabola being adjacent the first circle section; the trailing edge region being formed of a second circle section adjacent the first parabola section; and the pressure side region being formed of a third circle section adjacent the first ellipse section and a second parabola section of a second second-order parabola being disposed between the second circle section and the third circle section. The invention consists in a steam turbine (1) comprising a stationary cylinder (2) for containing a steam flow (6, 7, 8), and a rotor (3) enclosed by said cylinder, a row of blades (5), each of said blades being characterized by a root portion (12) attached to said rotor and an airfoil portion (11), each of said airfoil portions having (i) a base portion (15) and a tip portion (16) defining an airfoil height therebetween, (ii) a rounded leading edge portion (22) connecting the pressure surface (18) with the suction surface (14) and a trailing edge (26), (iii) a pressure surface (18) and a generally concave suction (14) surface extending between said rounded leading edge portion and said trailing edge and defining a thickness of said airfoil therebetween, the leading edge portion (22) connecting the pressure surface (18) with the suction surface (14), said pressure surface over at least a first portion of said airfoil height having a curvature undergoing an inflection at a location (48) disposed in a central portion of the airfoil height from a height of approximately 25% of the airfoil height to a height of approximately 75% of the airfoil height , a first portion (47) of said pressure surface extending over said first portion of said airfoil height having a concave curvature and being disposed between said inflection location and said rounded leading edge portion, a second portion (44) of said pressure surface extending over said first portion of said airfoil height having a convex curvature and being disposed between said inflection location, and said trailing edge, said concave curvature in said first portion of said pressure surface having a maximum negative value in excess of -0.03mm 1 , said convex curvature in said second portion of said pressure surface having a maximum positive value in excess of +0.03mm 1 In another aspect of the invention a steam turbine is characterized by a row of blades comprising an airfoil for each blade, each of said airfoils (i) having a base portion and a tip portion defining an airfoil height therebetween, (ii) having transverse sections disposed radially outward from said base by distances equal to 25%, 50% and 75%, respectively, of said height of said airfoil, and (iii) defined by the following parameters having approximately the values indicated below, all angles being expressed in degrees: Percent Height 25% 50% 75% Width (cm) 4.6 4.1 3.6 Pitch/Width Ratio 1.24 1.46 1.78 Pitch/Cord Ratio 0.85 0.86 0.87 Stagger Angle 46.4 53.8 60.5 Max Thickness/Cord 0.24 0.18 0.10 Camber Angle 101 81.2 62.4 Exit Opening (mm) 14.0 15.3 17.0 Inlet Metal Angle 65.1 85.1 105.0 Inlet Included Angle 50.7 55.7 43.8 Suction Surface Turning Angle 12.6 14.8 19.8 BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a portion of a cross-section through a steam turbine in the vicinity of the transition zone showing the blade according to the current invention, along with the adjacent vanes. Figure 2 is a schematic diagram of two adjacent, typical steam turbine blades illustrating various performance related parameters. Figure 3 is a cross-section taken along lines III-III shown in Figure 1. Figure 4 is a stack plot of transverse cross-sections through the blade shown in Figure 1 at various radial locations. Figure 5 is a graph showing the radial distribution of the inlet included angle IIA and pitch to width ratio P/W for the blade according to the current invention as a percentage of the airfoil height, from the base B of the airfoil to the tip T. Figure 6 is an enlarged view of the blade transverse cross-section at mid-height shown in Figure 3. Figure 7 is a graph showing the curvature K, in mm -1 x10 -2 , of the pressure surface of the airfoil of current invention from a point adjacent the trailing edge, indicated by reference numeral 40 in Figure 4, to a point adjacent the leading edge, indicated by reference numeral 42 in Figure 4, as a percent of the distance along the pressure surface between these two points at the three radial locations, the base B, the 50% height section, and the tip T. Figures 8 is graph showing the calculated axial distribution of the steam velocity ratio VR -- that is, the local surface velocity to the blade row exit velocity -- along the width W of the airfoil, from the leading edge LE to the trailing edge TE, over the blade suction surface, indicated by the circles, and the blade pressure surface, indicated by the squares, at the mid-height location. Referring to the drawings, there is shown in Figure 1 a portion of a longitudinal cross-section through the low pressure section of a steam turbine 1 in the vicinity of the transition zone. As shown, the steam flow path of the steam turbine 1 is formed by a stationary cylinder 2 and a rotor 3. A row of blades 5 are attached to the periphery of the rotor 3 and extend radially outward into the flow path in a circumferential array. A row of vanes 4 of a diaphragm structure are attached to the cylinder 2 and extend radially inward in a circumferential array immediately upstream of the row of blades 5. As previously discussed, the vanes 4 have airfoils 36 that cause the steam 6 to undergo a portion of the stage pressure drop as it flows through the row of vanes. The vane airfoils 36 also serve to direct the flow of steam 6 entering the stage so that the steam 7 enters the row of blades 5 at the correct angle. A second row of vanes 9 is disposed immediately downstream of the blades 5 and serves to direct the flow of steam 8 exiting the stage to the correct angle for the following row of blades (not shown). As shown in Figure 1, each blade 5 is comprised of an airfoil portion 11 that extracts energy from the steam 7, a root portion 12 that serves to fix the blade to the rotor 3 via a groove 37 formed therein, and a shroud 13 that is integrally formed at the airfoil tip 16 (such an integral shroud is disclosed in U.S. Patent No. 4,533,298 (Partington et al.), assigned to the same assignee as the current invention and herein incorporated by reference in its entirety). The integral shroud 13, in conjunction with a seal 17, serves to minimize the leakage of steam past the blade row. The airfoil 11 has a base portion 15 at its proximal end adjacent the root 12 -- that is, the base is the portion of the airfoil that forms an intersection with the root 12. The airfoil 11 also has a tip portion 16 at its distal end -- that is, the tip is the portion of the airfoil that forms an intersection with the shroud 13. The current invention concerns the airfoil 11 of the blade 5. More specifically, the current invention concerns a novel airfoil shape that greatly reduces the weight of the airfoil while maintaining adequate thermodynamic performance. As shown in Figure 6, each airfoil has a leading edge 22, a trailing edge 26, a concave suction surface 14 and a pressure surface 18 that has both concave and convex portions, as discussed further below. (As used herein, the term "leading edge" refers to the radiused portion of the airfoil 11 that connects the pressure surface 18 with the suction surface 14 at the upstream edge of the airfoil -- that is, the portion between locations 42 and 42' in Figure 6. Similarly, the term "trailing edge" refers to the radiused portion of the airfoil 11 that connects the pressure surface 18 with the suction surface 14 at the downstream edge of the airfoil -- that is, the portion between locations 40 and 40' in Figure 6.) The novel geometry of the airfoil 11 for the blade of the current invention is specified in Tables I-IV by the relevant parameters, each of which is discussed below (all angles in Tables I and IA are expressed in degrees), and illustrated in Figures 4 and 6. In Table I, each parameter is specified at three radial stations along the airfoil -- specifically, (i) at 25% height, corresponding to a radius from the center line of the rotor 3 of 91 cm (36 in), (ii) at mid-height, corresponding to a radius of 96 cm (38 in), and (iii) at 75% height, corresponding to a radius of 101 cm (40 in). Note, as used herein, percent height is defined with reference to the radial distance between the projected base and tip sections of the airfoil, as discussed below -- that is, as a percentage of the distance from the base 15 of the airfoil 11 where its leading edge 22 intersects the root 12 to the tip 16 of the airfoil where its trailing edge 26 intersects the shroud. Airfoil Parameters Percent Height 25% Section 50% Section 75% Section Radius (cm) 91 96 101 Width (cm) 4.6 4.1 3.6 Pitch/Width Ratio 1.24 1.46 1.78 Pitch/Cord Ratio 0.85 0.86 0.87 Stagger Angle 46.4 53.8 60.5 Max Thickness/Cord 0.24 0.18 0.10 Camber Angle 101 81.2 62.4 Exit Opening (mm) 14.0 15.3 17.0 Inlet Metal Angle 65.1 85.1 105.0 Inlet Included Angle 50.7 55.7 43.8 Suction Surface Turning Angle 12.6 14.8 19.8 As shown in Figure 1, both the tip 16 and the base 15 of the airfoil 11 are inclined at an angle to the axial direction. Thus, a cross-section through the airfoil tip 16 and base 15 would also be inclined at an angle to the axial direction, rather than lying in a single plane parallel to the axis of the rotor 3. Moreover, as shown in Figure 3, fillets 38 and 39 are formed at the intersections between the airfoil 11 and the shroud 13 and between the airfoil and the root 12. These fillets distort the actual blade geometry in a manner that is, by and large, irrelevant to its thermodynamic performance. Therefore, for purposes of establishing an airfoil's geometry, blade designers typically consider the tip cross-section to be the cross-section of the airfoil, ignoring the fillet 38, extrapolated up to a plane parallel to the axis of the rotor 3 and located at the intersection of the trailing edge 26 and the shroud 13. The airfoil base cross-section is considered to be the cross-section of the airfoil, ignoring the fillet 39, extrapolated down to a plane parallel to the axis of the rotor 3 and located at the intersection of the leading edge 22 and the root 12. Thus, to further define the airfoils parameters of the blade according to the current invention, Table IA shows the same parameters at four additional radial stations. Two of these radial stations are in the base portion 15 -- specifically, (i) the airfoil cross-section, extrapolated to a plane oriented parallel to the axis of the rotor 3, located at the intersection between the leading edge 22 and the root 12 ("projected base"), corresponding to a radius of 86 cm (33.9 in) and (ii) the location just above the fillet 39, indicated by line 45 in Figure 3, corresponding to a radius of 87 cm (34.3 in). The remaining two radial stations are in the tip portion 16 -- specifically, (i) the location just below the fillet 38, indicated by line 46 in Figure 3, corresponding to a radius of 104 cm (41.0 in) and (ii) the airfoil cross-section, extrapolated to a plane oriented parallel to the rotor axis, located at the intersection between the trailing edge 26 and the tip ("projected tip"), corresponding to a radius of 106 cm (41.7 in). Airfoil Parameters Section Location Projected Base Above Fillet Below Shroud Projected Tip Radius (cm) 86 87 104 106 Width (cm) 5.1 5.0 3.2 3.0 Pitch/width Ratio 1.06 1.10 2.06 2.23 Pitch/Chord Ratio 0.83 0.83 0.88 0.88 Stagger Angle 38.1 39.8 64.7 66.7 Max Thickness/Chord 0.33 0.30 0.08 0.07 Camber Angle 119 116 45.4 37.6 Exit Opening (mm) 12.6 12.9 18.4 18.8 Inlet Metal Angle 46.7 50.0 120 127 Inlet Included Angle 41.3 41.3 30.8 29.2 Suction Surface Turning Angle 11.0 11.6 17.4 14.1 The parameters shown in Tables I and IA are defined as follows, with reference to Figure 2. (It should be noted that Figure 2 illustrates the various parameters described below on a steam turbine blade airfoil of generalized cross-section. Reference should be made to Figures 4 and 6 for an illustration of the airfoil shape of the blade of the current invention at various defined transverse sections.) The chord of the blade is the distance from the leading edge 22 to the trailing edge 26 and is indicated as C in Figure 2. The width of the blade refers to the distance from the leading to the trailing edge in the axial direction -- that is, the axial component of the chord -- and is indicated by W in Figure 2. The pitch is the distance in the tangential direction between the trailing edges of adjacent blades and is indicated in Figure 2 as P. At any given diameter, the fewer the number of blades, the larger the pitch. In order to reduce the centrifugal force on the rotor 3, the number of blades in the row has been reduced. As a result, the pitch to chord and pitch to width ratios have been increased over conventional blades. Thus, as shown in Figure 5, the pitch to width ratio, P/W, exceeds 1.0 over the entire blade height. However, increasing the pitch makes it difficult to control the velocity distribution, thereby creating the potential for boundary layer separation as the steam expands toward the trailing edge 26 due to excessive deceleration. The stagger angle is the angle that a line 21 drawn from the leading edge 22 to the trailing edge 26 makes with the axial direction and is indicated in Figure 2 as S. As shown, the stagger angle was increased beyond conventional values in order to increase the pitch without losing control of steam velocity. The maximum thickness to chord ratio is the ratio of the maximum thickness of the airfoil transverse cross-section at the radial station to the chord length at that station. The quantity (1 - (maximum thickness/pitch)) is defined as the blockage. The reduced thickness and high pitch of the blade according to the current invention results in relatively high blockage. The camber angle is indicated as CA in Figure 2 and is defined by the angle between the leading and trailing edge portions of the airfoil. Thus, the camber angle may be expressed as by the equation CA = 180° - (IMA + EMA), where IMA and EMA are the inlet and exit metal angles, respectively. The inlet metal angle is defined below. The exit metal angle is the angle formed between the circumferential direction and the line 27 that bisects the lines 23 and 24, lines 23 and 24 being the lines that are tangent with the suction surface 11 and the pressure surface 18, respectively, at the trailing edge 26. The exit metal angle is indicated in Figure 2 as EMA. The exit opening, or throat, is the shortest distance from the trailing edge 26 of one blade to the suction surface 14 of the adjacent blade and is indicated in Figure 2 by O. The gauging of the blade row is defined as the ratio of the throat to the pitch and indicates the percentage of the annular area available for steam flow. The inlet metal angle is the angle formed between the circumferential direction and the line 25 that bisects the lines 19 and 20, lines 19 and 20 being the lines that are tangent with the suction surface 14 and the pressure surface 18, respectively, adjacent the leading edge 22. The inlet metal angle is indicated in Figure 2 as IMA. The inlet included angle is the angle between the tangent lines 19 and 20 and is indicated in Figure 2 as IIA. As discussed further below, the novel shape of the airfoil 11 of the current invention allows for a relatively large inlet included angle, especially in the mid-height region of the airfoil, as shown in Figure 5. This large inlet included angle results in higher acceleration in the inlet portion of the passage between adjacent blades, thereby minimizing the potential for boundary layer separation which, as discussed below, is a source of energy loss. The suction surface turning angle is the amount of the suction surface turning from the throat O to the trailing edge 26 and is indicated in Figure 2 as STA. The optimum value for the suction surface turning angle depends on the Mach No. and is also a tradeoff since too large an amount of turning can cause flow separation and too little turning will prevent the steam flow from accelerating properly. As can be seen, the suction surface turning angle in the airfoil of the current invention is relatively high, reaching almost 20° at 75% blade height. However, the airfoil shape has been carefully contoured to ensure that boundary layer separation does not occur in the regions adjacent the trailing edge 26, as discussed further below, despite the high suction surface turning angle. According to the current invention, the airfoil has a very small cross-sectional area in order to reduce its mass and, therefore, the centrifugal force imposed on the blade root 12 and rotor groove 37 as a result of the weight of the airfoil. However, other things being equal, reducing the cross-sectional area of the airfoil reduces its bending strength. According to the current invention, this problem was solved by utilizing a relatively high camber angle, as shown in Tables I and IA, to provide the necessary bending stiffness, as well as a switch in curvature in the pressure surface 18 near the leading edge 22. A detailed view of the shape of the airfoil of the current invention at the mid-height location is shown in Figure 6. In addition, Tables II and III show the values of the curvature of the suction and pressure surfaces 14 and 18, respectively, at eleven locations, shown in Figure 6, spaced along these surfaces and at five radial locations. (The curvature values for the base and tip cross-sections shown in Tables II and III are based on the projected cross-sections, as previously discussed.) As used herein, curvature K is defined as the inverse of the radius of curvature R of the surface contour. The radius of curvature is defined as the distance from the surface to the center of curvature, the center of curvature being defined as the intersection of two lines normal to the surface as the points of intersection of the two normal lines with the surface are made to approach one another. Suction Surface Curvature, mm -1 (x10 -2 ) Location Base Section 25% Section 50% Section 75% Section Tip Section 0% 0.29 0.13 0.17 0.22 0.05 10% 0.29 0.12 0.16 0.22 0.05 20% 0.18 0.13 0.18 0.26 0.12 30% 0.22 0.18 0.23 0.27 0.23 40% 0.33 0.34 0.21 0.26 0.31 50% 2.17 0.91 0.61 0.51 0.36 60% 5.76 3.45 1.31 0.79 0.49 70% 6.85 7.68 5.82 2.98 0.95 80% 3.78 5.76 8.08 5.83 1.80 90% 0.82 2.52 3.58 6.02 5.24 100% 1.08 0.05 0.64 1.54 4.69 Pressure Surface Curvature, mm -1 (x10 -2 ) Location Base Section 25% Section 50% Section 75% Section Tip Section 0% 0.22 0.16 0.20 0.17 0.04 10% 0.22 0.15 0.20 0.17 0.03 20% 0.25 0.37 0.38 0.26 0.18 30% 0.82 0.48 0.48 0.38 0.20 40% 1.32 0.87 0.74 0.41 0.31 50% 3.38 1.36 1.51 0.76 0.43 60% 5.10 4.44 2.14 1.76 0.50 70% 4.79 5.62 3.07 2.56 0.64 80% 3.41 3.54 4.32 3.30 0.70 90% 2.08 0.68 0.86 0.47 1.07 100% 0.40 -1.81 -3.53 -2.37 1.53 The 0% locations shown in Tables II and III are slightly upstream from the trailing edge 26 and are taken as the points of intersection 40 and 40' between the radius that forms the trailing edge and pressure and suction surfaces 18 and 14, respectively, as shown in Figure 6. The 100% locations are somewhat downstream from the leading edge 22 and are taken as the points of intersection 42 and 42' between the radius that forms the leading edge and pressure and suction surfaces 18 and 14, respectively. The remaining points are spaced evenly between points 40/40' and 42/42'. The locations 10%, 20%, etc., refer to the distance from that location to the 40/40' point (depending on whether the suction or pressure surface is being referred to) measured along the surface of the transverse section at the particular height (i.e., base, 25%, etc.), expressed as the percentage of the distance between the 40 and 42 points or between the 40' and 42' points (again depending on whether the suction of pressure surface is being referred to) as measured along the surface of the transverse section at that height. As shown in Table III and Figure 6, and graphically in Figure 7, according to the current invention, the curvature of the pressure surface 18 has a point of inflection in the portion 47 of the pressure surface 18 adjacent the leading edge 22 so that the radius of curvature of the airfoil 11 switches sign from positive to negative. (As used herein the sign convention is arbitrarily chosen to indicate whether, from a given reference point, the curvature is concave (negative) or convex (positive).) This curvature change occurs in the central portion of the airfoil height -- i.e., from a height of approximately 25% of the airfoil height to a height of approximately 75%. Referring to Figures 6 and 7, it can be seen that at mid-height the portion 44 of the pressure surface 18 approximately 70-80% upstream from the trailing edge 26 has a curvature K in excess of +0.03 mm -1 , indicated by the radius of curvature R2 from center of curvature C2. However, the curvature of the immediately upstream portion 47 that extends to point 42 has a negative curvature that exceeds - 0.03 mm -1 , indicated by the radius of curvature R1 from center of curvature C1. The point of inflection 48 occurs approximately 90% upstream of the trailing edge 26, as shown in Figures 6 and 7. Thus, the pressure surface 18 forms a generally convex surface except in the portion 47 wherein it forms a concave surface. As shown in Table III and Figure 7, the reverse curvature -- i.e., the degree of concavity of the curvature -- of the pressure surface 18 is at a maximum at approximately mid-height and then tapers out as the airfoil extends radially in either direction. Thus, although the reverse, concave, curvature persists down to at least 25% height and up to at least 75% height, it tapers out completely at the base 15 and tip 16 portions, so that there is no reverse curvature in these section and the curvature remains positive throughout, as is conventional. This shaping is done because although the higher acceleration that results from the high inlet included angle accompanying reverse curvature is desirable in the middle portion of the blade height, as previously discussed, such acceleration is to be avoided near the tip and the base since it would tend to promote secondary flows and their attendant losses. The use of the reverse curvature in the portion 47 of the airfoil 11 results in an unusual high inlet included angle IIA, defined in Figure 2. As shown in Table I and IA and plotted in Figure 5, the inlet included angle exceeds 30 almost over the entire radial height of the airfoil 11. As a result, the airfoil 11 is especially thick adjacent its leading edge 22, thereby making it possible to considerably thin down the portion of the airfoil downstream of the reverse curvature portion 47. The novel shape of the blade airfoil 11 according to the current invention, as specified in Tables I-III and illustrated in Figures 4-7, allows the steam 7 to expand across the blade row with a minimum amount of energy loss. Major sources of loss in the blade row are surface friction and separation of the boundary layer on the suction surface of the blade. Thus, in the blade according to the current invention, friction losses are minimized by configuring the airfoil shape so as to maintain the velocity of the steam at relatively low values, as shown in Figure 8. Specifically, Figure 8 shows that the velocity ratio -- that is, the ratio of the steam velocity along the surface of the airfoil at a given radial station to the velocity of the steam exiting the blade row at that radial station -- on both the suction surface 14 and the pressure surface 18, indicated by the circles and squares, respectively, along the entire width of the airfoil is less than 1.2. Such advantageous velocity profiles are made possible by the blade surface contour. In addition, Figure 8 also shows that in the blade according to the current invention separation of the boundary layer is prevented by configuring the airfoil geometry to ensure that the steam does not decelerate too rapidly as it expands toward the trailing edge of the airfoil, note the gradual decline in the velocity ration at the suction surface downstream of 80% of the blade width. The mechanical properties of the blade are shown in Table IV (the base and tip sections are the projected sections, as previously discussed). The principal coordinate axes of the airfoil are indicated in Figure 2 as MIN and MAX. The minimum and maximum second moments of inertia about these axes are shown in Table II as by I min and I max , respectively. The radial distribution of I min and the cross-sectional area have a strong influence on the first vibratory mode. The radial distribution of I max and the cross-sectional area have a strong influence on the second vibratory mode. Hence, it is important that these values be adjusted so as to avoid resonance. The distances of the leading and trailing edges from the principal coordinate axes are designed by C. The angle the principal coordinate axis MIN makes with the axial direction is indicated in Figure 2 as PCA. Airfoil Mechanical Parameters Percent Height Base 25% 50% 75% Tip Angle of Principal Coordinate Axes 42 49 56 62 68 Cross-sectional Area, mm 2 815 578 458 287 233 I tor (mm 2 x10 3 ) 52.4 21.4 11.2 2.8 1.2 I min (mm 4 x10 3 ) 51.1 21.7 9.2 2.7 0.6 I max (mm 4 x10 3 ) 172 130 113 83 76 C min LE (mm) -2.2 -1.7 -1.3 -0.9 -0.5 C max LE (mm) 1.8 1.8 2.1 2.4 2.8 C min TE (mm) -18 -14 -10 -7.1 -3.2 C max TE (mm) -49 -50 -49 -49 -47

Claims: A steam turbine (1) comprising a stationary cylinder (2) for containing a steam flow (6, 7, 8), and a rotor (3) enclosed by said cylinder, a row of blades (5), each of said blades being characterized by a root portion (12) attached to said rotor and an airfoil portion (11), each of said airfoil portions having (i) a base portion (15) and a tip portion (16) defining an airfoil height therebetween, (ii) a rounded leading edge portion (22) connecting the pressure surface (18) with the suction surface (14) and a trailing edge (26), (iii) a pressure surface (18) and a generally concave suction (14) surface extending between said rounded leading edge portion and said trailing edge and defining a thickness of said airfoil therebetween, the leading edge portion (22) connecting the pressure surface (18) with the suction surface (14), said pressure surface over at least a first portion of said airfoil height having a curvature undergoing an inflection at a location (48) disposed in a central portion of the airfoil height from a height of approximately 25% of the airfoil height to a height of approximately 75% of the airfoil height , a first portion (47) of said pressure surface extending over said first portion of said airfoil height having a concave curvature and being disposed between said inflection location and said rounded leading edge portion, a second portion (44) of said pressure surface extending over said first portion of said airfoil height having a convex curvature and being disposed between said inflection location, and said trailing edge, said concave curvature in said first portion of said pressure surface having a maximum negative value in excess of -0.03mm 1 , said convex curvature in said second portion of said pressure surface having a maximum positive value in excess of +0.03mm 1 . The steam turbine according to claim 1, wherein said inflection location (48) occurs at point that is displaced from said trailing edge (26) along said pressure surface (18) by a distance equal to approximately 90% of the distance along said pressure surface from said trailing edge to said leading edge (22). The steam turbine according to claim 1, wherein said first portion (47) of said pressure surface (18) has a boundary that is adjacent to said rounded leading edge portion (22). The steam turbine according to claim 3, wherein said second portion (44) of said pressure surface (18) forms all of said pressure surface between said trailing edge (26) and said first portion (47). The steam turbine according to claim 1, wherein said first portion of said airfoil height extends between first and second sections of said airfoil, said first section being disposed radially inward from said second section and being displaced from said root portion (12) by a distance equal to at least 25% of said height of said airfoil (11). The steam turbine according to claim 5, wherein said second section of said airfoil is displaced from said root portion (12) by a distance equal to at least 75% of said height of said airfoil (11). The steam turbine according to claim 1, wherein said pressure surface (18) undergoes no inflection of said curvature over a second portion of said airfoil height. The steam turbine according to claim 7, wherein said second portion of said airfoil height is disposed radially inward from said first portion of said height, and wherein said pressure surface (18) undergoes no inflection of said curvature over a third portion of said airfoil height, said third portion of said airfoil height being disposed radially outward from said first portion of said height. The steam turbine according to claim 1, wherein (i) each of said airfoils (11) has transverse sections disposed radially outward from said root (12) by distances equal to 25%, 50% and 75%, respectively, of said height of said airfoil, and (ii) each of said airfoils is defined by the following parameters having approximately the values indicated below, all angles being expressed in degrees: Percent Height 25% Section 50% Section 75% Section Width (cm) 4.6 4.1 3.6 Pitch/Width Ratio 1.24 1.46 1.78 Pitch/Cord Ratio 0.85 0.86 0.87 Stagger Angle 46.4 53.8 60.5 Max Thickness/Cord 0.24 0.18 0.10 Camber Angle 101 81.2 62.4 Exit Opening (mm) 14.0 15.3 17.0 Inlet Metal Angle 65.1 85.1 105.0 Inlet Included Angle 50.7 55.7 43.8 Suction Surface Turning Angle 12.6 14.8 19.8 The steam turbine according to claim 1, wherein (i) each of said airfoils (11) has transverse sections disposed radially outward from said root (12) by distances equal to 25%, 50% and 75%, respectively, of said height of said airfoil, and (ii) said pressure surface has a curvature at said 25%, 50% and 75% sections as follows, the locations 0% through 100% referring to distances by which each respective location is displaced from said trailing edge (26) along said pressure surface expressed as a percentage of the total distance along said pressure surface from said trailing edge to said leading edge (22): Pressure Surface Curvature, mm -1 (x10 -2 ) Location 25% Section 50% Section 75% Section 0% 0.16 0.20 0.17 10% 0.15 0.20 0.17 20% 0.37 0.38 0.26 30% 0.48 0.48 0.38 40% 0.87 0.74 0.41 50% 1.36 1.51 0.76 60% 4.44 2.14 1.76 70% 5.62 3.07 2.56 80% 3.54 4.32 3.30 90% 0.68 0.86 0.47 100% -1.81 -3.53 -2.37 The steam turbine according to claim 11, wherein said suction surface (14) has a curvature at said 25%, 50% and 75% sections as follows, the locations 0% through 100% referring to distances by which each respective location is displaced from said trailing edge (26) along said suction surface expressed as a percentage of the total distance along said suction surface from said trailing edge to said leading edge (22): Suction Surface Curvature, mm -1 (x10 -2 ) Location 25% Section 50% Section 75% Section 0% 0.13 0.17 0.22 10% 0.12 0.16 0.22 20% 0.13 0.18 0.26 30% 0.18 0.23 0.27 40% 0.34 0.21 0.26 50% 0.91 0.61 0.51 60% 3.45 1.31 0.79 70% 7.68 5.82 2.98 80% 5.76 8.08 5.83 90% 2.52 3.58 6.02 100% 0.05 0.64 1.54

Inventors: CORNELL DANIEL RICHARD, FERLEGER JUREK, CORNELL, DANIEL RICHARD, FERLEGER, JUREK
Applicants: SIEMENS WESTINGHOUSE POWER, SIEMENS WESTINGHOUSE POWER CORPORATION
Application year: 1994
Main classification: F01D5
IPC codes: F01D5